CN106440460B - Supercooling system of air conditioner heat pump and working method of supercooling system - Google Patents
Supercooling system of air conditioner heat pump and working method of supercooling system Download PDFInfo
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- CN106440460B CN106440460B CN201610960781.8A CN201610960781A CN106440460B CN 106440460 B CN106440460 B CN 106440460B CN 201610960781 A CN201610960781 A CN 201610960781A CN 106440460 B CN106440460 B CN 106440460B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B13/00—Compression machines, plants or systems, with reversible cycle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B40/00—Subcoolers, desuperheaters or superheaters
- F25B40/02—Subcoolers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
- F25B47/02—Defrosting cycles
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/021—Indoor unit or outdoor unit with auxiliary heat exchanger not forming part of the indoor or outdoor unit
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
- F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2347/00—Details for preventing or removing deposits or corrosion
- F25B2347/02—Details of defrosting cycles
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2500/00—Problems to be solved
- F25B2500/18—Optimization, e.g. high integration of refrigeration components
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
The invention discloses an air conditioner heat pump supercooling system which comprises a compressor, a four-way valve, a first heat exchanger, a second heat exchanger, a third heat exchanger, a fourth heat exchanger, a first one-way valve, a second one-way valve, a first throttling part, a second throttling part, a third throttling part, a fourth throttling part, a liquid reservoir, a first stop valve and a second stop valve, wherein the four-way valve is provided with S, C, E, D four interfaces, the first heat exchanger is internally provided with a first heat exchange tube and a second heat exchange tube which are parallel and close to each other, the first heat exchange tube is provided with an interface a and an interface b, the second heat exchange tube is provided with an interface c and an interface d, the fourth heat exchange tube is internally provided with a third heat exchange tube and a fourth heat exchange tube which are parallel and close to each other, the third heat exchange tube is provided with an interface e and an interface f, the fourth heat exchange tube is provided with an interface g and an interface h, and a main flow path is formed by connecting the four heat exchange tubes, The enthalpy-increasing flow path and the enthalpy-increasing branch enable the supercooling system to have a supercooling function and a defrosting function.
Description
Technical Field
The invention relates to the technical field of air-conditioning heat pumps, in particular to an air-conditioning heat pump supercooling system and a working method thereof.
Background
Some refrigeration systems of the existing air energy heat pump products guide a liquid outlet pipe of a heat exchanger to the bottom of the heat exchanger for ice melting and supercooling, some refrigeration systems are provided with plate heat exchangers, and the refrigerant on a main flow path is supercooled by enthalpy-increasing branch refrigerant heat absorption evaporation, but the two supercooling modes are insufficient.
In the first scheme, when the ambient temperature is too high, frost cannot form on the heat exchanger, the supercooling pipe is supercooled by air in the environment, the supercooling efficiency is limited, in the supercooling process, heat taken away by the air is not absorbed and utilized, so that heat loss of a refrigeration system is caused, and the system heating quantity is influenced; and in the second scheme, when ambient temperature is higher than a certain value, the enthalpy-increasing branch on the refrigerating system is closed, the refrigerant flowing out of the heat exchanger does not exchange heat and cool when flowing through the plate heat exchanger, along with the increase of condensation temperature, the refrigerating capacity of the system is reduced, the power of the press is increased, the exhaust temperature is increased, the temperature of lubricating oil is increased, the viscosity is reduced, and the reliability and the service life of the operation of the compressor are directly influenced.
Disclosure of Invention
Aiming at the defects of the prior art, the invention aims to provide an air conditioner heat pump supercooling system which is capable of reducing the condensation temperature, high in operation reliability, long in service life, high in efficiency and energy-saving and a working method thereof.
In order to achieve the purpose, the scheme provided by the invention is as follows: an air-conditioning heat pump supercooling system comprises a compressor, a four-way valve, a first heat exchanger, a second heat exchanger, a third heat exchanger, a fourth heat exchanger, a first one-way valve, a second one-way valve, a first throttling component, a second throttling component, a third throttling component, a fourth throttling component, a liquid reservoir, a first stop valve and a second stop valve, the four-way valve is provided with S, C, E, D four interfaces, the first heat exchanger is internally provided with a first heat exchange tube and a second heat exchange tube which are parallel and close to each other, the first heat exchange tube is provided with a joint a and a joint b, the second heat exchange tube is provided with a joint c and a joint d, the fourth heat exchanger is internally provided with a third heat exchange tube and a fourth heat exchange tube which are parallel and close to each other, the third heat exchange tube is provided with an e interface and an f interface, the fourth heat exchange tube is provided with a g interface and an h interface, and a main flow path, an enthalpy-increasing flow path and an enthalpy-increasing branch are formed by connecting the parts;
the connection relationship of the components in the main flow path is as follows: the compressor is connected with the four-way valve interface D, the four-way valve interface C is connected with a second heat exchanger, the second heat exchanger is respectively connected with the third throttling component and the second one-way valve, and the third throttling component and the second one-way valve are jointly connected with an interface e of the fourth heat exchanger; the interface f of the fourth heat exchanger is connected with the liquid storage device;
the connection relation of each component in the enthalpy-increasing flow path is as follows: the liquid storage device is connected with a connector d of the first heat exchanger, a connector c of the first heat exchanger is respectively connected with the second throttling component and the first one-way valve, the second throttling component and the first one-way valve are jointly connected with the third heat exchanger, the third heat exchanger is connected with a connector E of the four-way valve, a connector S of the four-way valve is respectively connected with the fourth throttling component and the second stop valve, the fourth throttling component and the second stop valve are jointly connected with a connector h of the fourth heat exchanger, and a connector g of the fourth heat exchanger is connected with the compressor;
the main flow path and the enthalpy increasing flow path jointly form a main circulation loop of the supercooling system;
the connection relation of each component in the enthalpy-increasing branch is as follows: the reservoir is connected to the first stop valve, the first stop valve is connected to the first throttling member, the first throttling member is connected to a port a of the first heat exchanger, and a port b of the first heat exchanger is connected to the compressor.
The invention also provides a working method of the air-conditioning heat pump supercooling system, and the supercooling system has a supercooling function and a defrosting function;
when the outdoor environment temperature is lower than a set value, high-temperature and high-pressure refrigerant flows to a connector D of the four-way valve from the compressor, flows to the second heat exchanger from a connector C of the four-way valve to release heat and cool, flows to the second one-way valve after releasing heat and cooling, flows to a connector e of the fourth heat exchanger from the second one-way valve, releases heat and cools through the third heat exchange tube in the fourth heat exchanger, flows to the liquid accumulator from a connector f of the fourth heat exchanger, flows to a connector D of the first heat exchanger from the liquid accumulator and releases heat and cools through the second heat exchange tube, flows out from a connector C of the first heat exchanger after releasing heat and cooling, flows to the second throttling component for throttling, enters the third heat exchanger to absorb heat and evaporate, the heat-absorbing and evaporating refrigerant flows back to a connector E of the four-way valve and flows to the fourth throttling component through a connector S of the four-way valve for throttling, the throttled refrigerant flows to a connector h of the fourth heat exchanger, heat released by the refrigerant in the third heat exchange tube is absorbed in the fourth heat exchanger through the fourth heat exchange tube, the heat-absorbing and evaporating refrigerant flows back to the compressor from a connector g of the fourth heat exchanger, and the supercooling function of the main flow path and the enthalpy-increasing flow path is completed; meanwhile, a first stop valve on the enthalpy-increasing branch is opened to divide the refrigerant flowing out of the liquid reservoir into two parts, one part of the refrigerant flows to a connector d of the first heat exchanger, the other part of the refrigerant flows to the first stop valve and then flows to the first throttling part for throttling, the throttled refrigerant flows to a connector a of the first heat exchanger and enters the first heat exchanger to absorb heat released by the refrigerant in the second heat exchange tube through the first heat exchange tube, and the refrigerant after heat absorption and evaporation flows back to the compressor through a connector b of the first heat exchanger to finish the supercooling function of the enthalpy-increasing branch;
when the supercooling system needs to defrost the third heat exchanger, high-temperature and high-pressure refrigerant flows to a connector D of the four-way valve through the compressor, flows to the third heat exchanger from a connector E of the four-way valve to release heat and defrost, flows to the first one-way valve after heat release and defrost, flows to a connector C of the first heat exchanger through the first one-way valve, flows to the liquid storage device from a connector D of the first heat exchanger, flows to a connector f of the fourth heat exchanger through the liquid storage device, flows out from a connector E of the fourth heat exchanger, flows to the third throttling component to be throttled, enters the second heat exchanger to absorb heat and evaporate, flows to a connector C of the four-way valve after heat absorption and evaporation, flows out from a connector S of the four-way valve and flows through the second stop valve, then flows to the interface h of the fourth heat exchanger, and then flows back to the compressor from the interface g of the fourth heat exchanger, thus completing the defrosting function of the supercooling system.
The beneficial effect of this scheme does: 1. the refrigerating capacity and the energy efficiency ratio are improved, the supercooling degree of the system can be improved and the condensing temperature of a refrigerant is reduced through the double supercooling design, so that the refrigerating capacity and the energy efficiency ratio of the refrigerating system are improved; 2. the supercooling degree of the main flow refrigerant is improved, and the supercooling degree of the main flow refrigerant before entering the heat exchanger can be improved by the first heat absorption of the refrigerant at the outlet of the heat exchanger and the second heat absorption of the enthalpy-increasing branch refrigerant; 3. the supercooling degree of the refrigerant of the enthalpy-increasing branch is improved, the refrigerant at the outlet of one heat exchanger absorbs the waste heat of the refrigerant at the outlet of the other heat exchanger, and the supercooling degree of the refrigerant entering the enthalpy-increasing branch can be improved; 4. the liquid impact is prevented, and the refrigerant at the outlet of one heat exchanger absorbs the waste heat of the refrigerant at the outlet of the other heat exchanger, so that the compressor is prevented from being impacted by liquid impact; 5. the application range is wide: through the design of low-temperature enthalpy increase, the air-conditioning heat pump system is suitable for the environment temperature of minus 25 ℃ to 43 ℃.
Drawings
FIG. 1 is a schematic diagram of the present invention.
Fig. 2 is a schematic view of the supercooling operation of the present invention.
Fig. 3 is a schematic view illustrating a defrosting operation according to the present invention.
Wherein, 1 is a compressor, 2 is a four-way valve, 31 is a first heat exchanger, 311 is a first heat exchange tube, 312 is a second heat exchange tube, 32 is a second heat exchanger, 33 is a third heat exchanger, 34 is a fourth heat exchanger, 341 is a third heat exchange tube, 342 is a fourth heat exchange tube, 41 is a first check valve, 42 is a second check valve, 51 is a first throttling component, 52 is a second throttling component, 53 is a third throttling component, 54 is a fourth throttling component, 6 is a reservoir, 71 is a first stop valve, and 72 is a second stop valve.
Detailed Description
The invention will be further illustrated with reference to specific examples:
referring to fig. 1, the supercooling system of the air-conditioning heat pump and the working method thereof comprises a compressor 1, a four-way valve 2, a first heat exchanger 31, a second heat exchanger 32, a third heat exchanger 33, a fourth heat exchanger 34, a first check valve 41, a second check valve 42, a first throttling part 51, the four-way valve 2 is provided with S, C, E, D four interfaces, a first heat exchange tube 311 and a second heat exchange tube 312 which are parallel and close to each other are arranged in the first heat exchanger 31, the first heat exchange tube 311 is provided with an interface a and an interface b, the second heat exchange tube 312 is provided with an interface c and an interface d, a third heat exchange tube 341 and a fourth heat exchange tube 342 which are parallel and close to each other are arranged in the fourth heat exchanger 34, the third heat exchange tube 341 is provided with an interface e and an interface f, and the fourth heat exchange tube 342 is provided with an interface g and an interface h.
The connection of the components of the subcooling system of the present embodiment is as follows:
the compressor 1 is connected with a four-way valve 2 interface D, a four-way valve 2 interface C is connected with the second heat exchanger 32, the second heat exchanger 32 is respectively connected with a third throttling component 53 and a second one-way valve 42, and the third throttling component 53 and the second one-way valve 42 are jointly connected with an interface e of the fourth heat exchanger 34; the port f of the fourth heat exchanger 34 is connected to the accumulator 6, forming the main flow path of the subcooling system.
The reservoir 6 is connected with a port d of the first heat exchanger 31, a port c of the first heat exchanger 31 is respectively connected with the second throttling component 52 and the first one-way valve 41, the second throttling component 52 and the first one-way valve 41 are commonly connected with the third heat exchanger 33, the third heat exchanger 33 is connected with a port E of the four-way valve 2, a port S of the four-way valve 2 is respectively connected with the fourth throttling component 54 and the second stop valve 72, the fourth throttling component 54 and the second stop valve 72 are commonly connected with a port h of the fourth heat exchanger 34, a port g of the fourth heat exchanger 34 is connected with the compressor 1 to form an enthalpy-increasing flow path of the supercooling system, and the main flow path and the enthalpy-increasing flow path jointly form a main circulation loop of the supercooling system.
The accumulator 6 is further connected with a first stop valve 71, the first stop valve 71 is connected with a first throttling part 51, the first throttling part 51 is connected with a port a of the first heat exchanger 31, and a port b of the first heat exchanger 31 is connected with the compressor 1 to form an enthalpy-increasing branch of the supercooling system.
The supercooling system of the present embodiment has supercooling and defrosting functions through the above connection, and the two functions are implemented as follows:
referring to fig. 2, when the outdoor temperature is lower than the set value, the high-temperature and high-pressure refrigerant flows from the compressor 1 to the port D of the four-way valve 2, flows from the port C of the four-way valve 2 to the second heat exchanger 32 to release heat and cool, flows to the second check valve 42, flows from the second check valve 42 to the port E of the fourth heat exchanger 34, flows through the third heat exchange tube 341 in the fourth heat exchanger 34 to release heat and cool, flows from the port f of the fourth heat exchanger 34 to the accumulator 6, flows from the accumulator 6 to the port D of the first heat exchanger 31 to release heat and cool through the second heat exchange tube 312, flows out from the port C of the first heat exchanger 31 to the second throttling part 52 to throttle, flows into the third heat exchanger 33 to evaporate, flows back to the port E of the four-way valve 2 to absorb heat and evaporate, the refrigerant after throttling flows to the fourth throttling component 54 through the interface S of the four-way valve 2, flows to the interface h of the fourth heat exchanger 34, absorbs the heat released by the refrigerant in the third heat exchange tube 341 through the fourth heat exchange tube 342 in the fourth heat exchanger 34, and the refrigerant after heat absorption and evaporation flows back to the compressor 1 from the interface g of the fourth heat exchanger 34, so as to complete the supercooling function of the main flow path and the enthalpy increasing flow path; meanwhile, the first stop valve 71 on the enthalpy-increasing branch is opened to divide the refrigerant flowing out of the liquid reservoir 6 into two parts, one part of the refrigerant flows to the interface d of the first heat exchanger 31, the other part of the refrigerant flows to the first stop valve 71 and then flows to the first throttling part 51 for throttling, the throttled refrigerant flows to the interface a of the first heat exchanger 31 and enters the first heat exchanger 31 to absorb heat released by the refrigerant in the second heat exchange tube 312 through the first heat exchange tube 311, the refrigerant after heat absorption and evaporation flows back to the compressor 1 through the interface b of the first heat exchanger 31 to complete the supercooling function of the enthalpy-increasing branch, and the system completes the multiple supercooling function through the circulation of the main flow path, the enthalpy-increasing flow path and the enthalpy-increasing branch.
Referring to fig. 3, when the supercooling system needs to defrost the third heat exchanger 33, a high-temperature and high-pressure refrigerant flows from the compressor 1 to the port D of the four-way valve 2, flows from the port E of the four-way valve 2 to the third heat exchanger 33 for heat release and defrosting, flows to the first check valve 41, flows from the first check valve 41 to the port C of the first heat exchanger 31, flows from the port D of the first heat exchanger 31 to the accumulator 6, flows from the accumulator 6 to the port f of the fourth heat exchanger 34, flows out from the port E of the fourth heat exchanger 34, flows to the third throttling part 53 for throttling, flows into the second heat exchanger 32 for heat absorption and evaporation, flows to the port C of the four-way valve 2, flows out from the port S of the four-way valve 2, flows through the second stop valve 72, and flows to the port h of the fourth heat exchanger 34, then flows back to the compressor 1 from the port g of the fourth heat exchanger 34, and the defrosting function of the supercooling system is completed.
The functional principle of the embodiment is as follows:
according to the main flow path supercooling principle, the refrigerant at the outlet of one heat exchanger absorbs the waste heat of the refrigerant at the outlet of the other heat exchanger, so that the condensation temperature of the refrigerant is reduced, and the primary supercooling function is realized; and then the refrigerant before entering the heat exchanger is subjected to heat absorption and supercooling again by the enthalpy-increasing flow path refrigerant, so that the condensation temperature of the refrigerant before flowing into the heat exchanger is further reduced, and the double supercooling function is realized.
The enthalpy-increasing flow path supercooling principle is adopted, and a refrigerant at the outlet of a heat exchanger is used for absorption; the residual heat of the refrigerant at the outlet of the other heat exchanger reduces the condensation temperature of the refrigerant, realizes the primary supercooling function, thereby reducing the condensation temperature of the refrigerant before flowing into the enthalpy-increasing branch and realizing the supercooling function of the enthalpy-increasing branch.
The liquid impact prevention principle is that the refrigerant at the outlet of one heat exchanger exchanges heat with the refrigerant at the outlet of the other heat exchanger, namely, the refrigerant at the outlet of one heat exchanger absorbs the residual heat of the refrigerant at the outlet of the other heat exchanger to evaporate, so that the liquid of the refrigerant which is not evaporated enters the compressor 1 to cause the liquid impact of the compressor 1.
According to the enthalpy-increasing branch principle, when the ambient temperature is lower than a certain value, the first stop valve 71 of the enthalpy-increasing branch is controlled to be opened, the refrigerant is throttled by the first throttling component 51, the first heat exchange tube 311 absorbs the waste heat of the refrigerant after primary supercooling in the second heat exchange tube 312 in the first heat exchanger 31 to evaporate, the refrigerant after heat absorption and evaporation flows back to the compressor 1, the refrigerant circulation amount of the refrigeration system is increased, and the normal operation of the system is ensured.
The way of absorbing the waste heat of the refrigerant at the outlet of the other heat exchanger by the refrigerant at the outlet of the one heat exchanger is to absorb the waste heat of the refrigerant at the outlet of the second heat exchanger 32 by the refrigerant at the outlet of the third heat exchanger 33 through the fourth heat exchanger 34 in this embodiment, so as to reduce the condensation temperature of the refrigerant and realize the primary supercooling function.
The supercooling system of the embodiment controls the circulating flow path through the valve bodies such as the four-way valve 2, the two one-way valves, the two stop valves and the like, but the system is not limited by the valve bodies, and the valve bodies are selected based on actual requirements.
The above description is only for explaining the composition form, functional principle and partial function implementation of the supercooling system of the air-conditioning heat pump, and is not limited to the change of the structure composition and the type of the used material, and all methods of using the refrigerant at the outlet of one heat exchanger to absorb the waste heat of the refrigerant at the outlet of another heat exchanger together with the invention are within the protection scope of the present application.
Claims (2)
1. An air conditioner heat pump supercooling system, which is characterized by comprising the following components: the heat exchanger comprises a compressor (1), a four-way valve (2), a first heat exchanger (31), a second heat exchanger (32), a third heat exchanger (33), a fourth heat exchanger (34), a first one-way valve (41), a second one-way valve (42), a first throttling part (51), a second throttling part (52), a third throttling part (53), a fourth throttling part (54), a liquid reservoir (6), a first stop valve (71) and a second stop valve (72), wherein the four-way valve (2) is provided with S, C, E, D four interfaces, a first heat exchange tube (311) and a second heat exchange tube (312) which are parallel and close to each other are arranged in the first heat exchanger (31), the first heat exchange tube (311) is provided with an a interface and a interface, the second heat exchange tube (312) is provided with a c interface and a interface, and a fourth heat exchange tube (342) which are parallel and close to each other are arranged in the fourth heat exchanger (34), the third heat exchange tube (341) is provided with interfaces e and f, the fourth heat exchange tube (342) is provided with interfaces g and h, and a main flow path, an enthalpy-increasing flow path and an enthalpy-increasing branch are formed by connecting the above components; the connection relationship of the components in the main flow path is as follows: the compressor (1) is connected with a port D of the four-way valve (2), a port C of the four-way valve (2) is connected with a second heat exchanger (32), the second heat exchanger (32) is respectively connected with the third throttling component (53) and a second one-way valve (42), and the third throttling component (53) and the second one-way valve (42) are jointly connected with a port e of the fourth heat exchanger (34); the interface f of the fourth heat exchanger (34) is connected with the liquid storage device (6); the connection relation of each component in the enthalpy-increasing flow path is as follows: the reservoir (6) is connected with a port d of the first heat exchanger (31), a port c of the first heat exchanger (31) is respectively connected with the second throttling component (52) and the first one-way valve (41), the second throttling component (52) and the first one-way valve (41) are jointly connected with the third heat exchanger (33), the third heat exchanger (33) is connected with a port E of the four-way valve (2), a port S of the four-way valve (2) is respectively connected with the fourth throttling component (54) and the second stop valve (72), the fourth throttling component (54) and the second stop valve (72) are jointly connected with a port h of the fourth heat exchanger (34), and a port g of the fourth heat exchanger (34) is connected with the compressor (1); the main flow path and the enthalpy increasing flow path jointly form a main circulation loop of the supercooling system; the connection relation of each component in the enthalpy-increasing branch is as follows: the accumulator (6) is connected to the first stop valve (71), the first stop valve (71) is connected to the first throttle member (51), the first throttle member (51) is connected to a port a of the first heat exchanger (31), and a port b of the first heat exchanger (31) is connected to the compressor (1).
2. A method of operating an air conditioning heat pump subcooling system as described in claim 1, wherein: the supercooling system has a supercooling function and a defrosting function; when the outdoor environment temperature is lower than a set value, a high-temperature and high-pressure refrigerant flows to a connector D of the four-way valve (2) from the compressor (1), flows to the second heat exchanger (32) from a connector C of the four-way valve (2) to release heat and cool, flows to the second one-way valve (42) and then flows to a connector e of the fourth heat exchanger (34) from the second one-way valve (42), the refrigerant releases heat and cools in the fourth heat exchanger (34) through the third heat exchange tube (341), flows to the liquid accumulator (6) from a connector f of the fourth heat exchanger (34), flows to a connector D of the first heat exchanger (31) from the liquid accumulator (6), releases heat and cools through the second heat exchange tube (312), and flows out from a connector C of the first heat exchanger (31), the refrigerant after throttling flows into the second throttling component (52) for throttling, enters the third heat exchanger (33) for absorbing heat and evaporating, flows back to a connector E of the four-way valve (2) and flows to the fourth throttling component (54) through a connector S of the four-way valve (2) for throttling, flows to a connector h of the fourth heat exchanger (34) and absorbs heat released by the refrigerant in the third heat exchange tube (341) through the fourth heat exchange tube (342) in the fourth heat exchanger (34), and flows back to the compressor (1) from a connector g of the fourth heat exchanger (34) to finish the supercooling function of a main flow path and an enthalpy increasing flow path; meanwhile, a first stop valve (71) on the enthalpy-increasing branch is opened, so that the refrigerant flowing out of the liquid reservoir (6) is divided into two parts, one part of the refrigerant flows to a connector d of the first heat exchanger (31), the other part of the refrigerant flows to the first stop valve (71), the refrigerant flows to the first throttling component (51) for throttling, the throttled refrigerant flows to a connector a of the first heat exchanger (31) and enters the first heat exchanger (31) to absorb heat released by the refrigerant in the second heat exchange tube (312) through the first heat exchange tube (311), the refrigerant after heat absorption and evaporation flows back to the compressor (1) through the connector b of the first heat exchanger (31), and the supercooling function of the enthalpy-increasing branch is completed; when the supercooling system needs to defrost the third heat exchanger (33), a high-temperature and high-pressure refrigerant flows to a connector D of the four-way valve (2) from the compressor (1), flows to the third heat exchanger (33) from a connector E of the four-way valve (2) for heat release and defrosting, flows to the first one-way valve (41) from the connector E of the four-way valve (2), flows to a connector c of the first heat exchanger (31) from the first one-way valve (41), flows to the liquid accumulator (6) from the connector D of the first heat exchanger (31), flows to a connector f of the fourth heat exchanger (34) from the liquid accumulator (6), flows out from a connector E of the fourth heat exchanger (34) to the third throttling component (53) for throttling, and enters the second heat exchanger (32) for heat absorption and evaporation after throttling, and the refrigerant after heat absorption and evaporation flows to a connector C of the four-way valve (2), flows out of a connector S of the four-way valve (2), flows through the second stop valve (72), flows to a connector h of the fourth heat exchanger (34), and then flows back to the compressor (1) from a connector g of the fourth heat exchanger (34), so that the defrosting function of the supercooling system is completed.
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| CN106979638A (en) * | 2017-04-28 | 2017-07-25 | 上海理工大学 | Automobile air-conditioning evaporator defroster |
| CN112432399B (en) * | 2020-12-08 | 2022-07-01 | 合肥美的暖通设备有限公司 | Air conditioning system |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN202382480U (en) * | 2011-11-22 | 2012-08-15 | 广东芬尼克兹节能设备有限公司 | Air-injection enthalpy-increasing type heat pump |
| JPWO2010100707A1 (en) * | 2009-03-02 | 2012-09-06 | 三菱電機株式会社 | Air conditioner |
| CN102679609A (en) * | 2012-06-07 | 2012-09-19 | 四川同达博尔置业有限公司 | Air-cooled heat pump air conditioner |
| CN203857718U (en) * | 2014-05-23 | 2014-10-01 | 青岛海尔空调电子有限公司 | Air-conditioning system |
| CN204555425U (en) * | 2015-01-22 | 2015-08-12 | 宁波赛森节能设备有限公司 | A kind of ultra-low-loop temperature air source heat pump with backheat |
| CN205641295U (en) * | 2016-04-18 | 2016-10-12 | 广东高而美制冷设备有限公司 | Frostproofing subcooling increases enthalpy air conditioner heat transfer system |
| CN206269413U (en) * | 2016-10-26 | 2017-06-20 | 广东高而美制冷设备有限公司 | A kind of air-conditioning heat pump crosses cooling system |
-
2016
- 2016-10-26 CN CN201610960781.8A patent/CN106440460B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPWO2010100707A1 (en) * | 2009-03-02 | 2012-09-06 | 三菱電機株式会社 | Air conditioner |
| CN202382480U (en) * | 2011-11-22 | 2012-08-15 | 广东芬尼克兹节能设备有限公司 | Air-injection enthalpy-increasing type heat pump |
| CN102679609A (en) * | 2012-06-07 | 2012-09-19 | 四川同达博尔置业有限公司 | Air-cooled heat pump air conditioner |
| CN203857718U (en) * | 2014-05-23 | 2014-10-01 | 青岛海尔空调电子有限公司 | Air-conditioning system |
| CN204555425U (en) * | 2015-01-22 | 2015-08-12 | 宁波赛森节能设备有限公司 | A kind of ultra-low-loop temperature air source heat pump with backheat |
| CN205641295U (en) * | 2016-04-18 | 2016-10-12 | 广东高而美制冷设备有限公司 | Frostproofing subcooling increases enthalpy air conditioner heat transfer system |
| CN206269413U (en) * | 2016-10-26 | 2017-06-20 | 广东高而美制冷设备有限公司 | A kind of air-conditioning heat pump crosses cooling system |
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|---|---|
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